Walk power mower with biased handle

ABSTRACT

A walk power mower having a cutting deck supported upon the ground by front and rear wheels. The mower includes a biased handle that permits the handle to be pivotally displaced downwardly, against an upward bias force, during operation. The bias force may be provided by a resilient member that compresses as the handle is displaced downwardly. The compression of the resilient member allows downward movement of the handle without initially producing corresponding upward movement of the front wheels of the mower during rearward pulling of the handle.

This application is a continuation-in-part of U.S. patent application Ser. No. 15/195,648, filed Jun. 28, 2016, the content of which is incorporated herein by reference in its entirety.

TECHNICAL FIELD

Embodiments of the present disclosure relate to a walk power mower for cutting grass and, more particularly, to a biased operator handle for use with such a mower.

BACKGROUND

Walk power mowers are well known for cutting grass. For example, such mowers are commonly used by property owners, such as homeowners, to cut their lawns. Such mowers have a cutting deck that houses a rotary grass cutting blade. The deck is supported by a plurality of wheels for rolling over the ground. A handle extends upwardly and rearwardly from the deck. A user who walks on the ground behind the deck grips a handle grip of the handle to manipulate and guide the mower during a grass mowing operation.

It can be difficult or is undesirable for some users to manually push a walk power mower over the ground in order to cut one's lawn. It is tiring to do so, particularly when the area being mowed is either large, hilly, or both. Thus, many mowers have traction drive systems that utilize part of the power generated by the prime mover carried on the mower to drive at least one pair of the mower's wheels, either the front wheels or the rear wheels, in a forward direction. Such a self-propelled mower relieves the user of the necessity of having to bodily push the mower over the ground. This greatly eases the physical effort required from the user in mowing one's lawn. The user now primarily guides or steers the mower during the powered forward motion provided by the traction drive system and the prime mover.

There are times when mowing one's lawn when the user needs to pull the mower in reverse at least over short distances. For example, when a user cuts grass under the branches of a bush, the user will ordinarily drive the mower forwardly so that the cutting blade reaches under the branches sufficiently to cut whatever patch of grass lies beneath the branches. However, once this patch of grass is cut, the user must pull back on the handle to pull the mower out from under the branches of the bush. While the traction drive system is designed with a one way clutch to allow the drive wheels to free-wheel during reverse motion so that the user is not pulling back against the resistance provided by the gearing in the traction drive system, the drive wheels of the mower are typically unpowered during this reverse motion.

As a result, many users end up having to manhandle or wrestle the mower back in this reverse motion scenario. This requires the user to expend physical energy and for some users accomplishing manual reverse motion of the mower may be difficult or impossible in some situations. This difficulty is exacerbated for those users in which trimming operations requiring reverse motions of the mower are numerous or are required on difficult terrain. For example, in trimming beneath a bush, pulling back on the mower is even more difficult if the user has to pull the mower back up a slope to get it out from under the branches of the bush.

Another problem sometimes present during reverse mower movement is unintentional lifting of the mower's front wheels. That is, when a pulling force is applied at the offset mower handle, a moment is produced that causes the mower to rotate about a line of contact between the ground and the rear wheels. As one can appreciate, this rotation may cause the mower's front wheels to lift. While such lifting of the front wheels may be beneficial for various mower operations (e.g., turning), maintaining front wheel engagement with the ground during reverse may be advantageous (e.g., to maintain quality of cut).

SUMMARY

One aspect of the present disclosure relates to a walk power mower including: a grass cutting deck surrounding a grass cutting member, wherein the cutting deck is adapted to travel over the ground in both a forward direction and a reverse direction; and a handle comprising an upwardly and rearwardly extending handle member. The handle member includes an upper end comprising a grip area, and a lower end pivotally attached to the cutting deck such that the handle member pivots about a transverse pivot axis within an operating range of pivotal motion defined by: an upper stop corresponding to the handle being in a first operating orientation; and a lower stop corresponding to the handle being in a second operating orientation, the operating range of pivotal motion being at least about 5 degrees. A resilient member is operatively positioned between the lower stop and the handle member, wherein the resilient member is adapted to bias the handle member to a location at or near the upper stop.

In another aspect, the present disclosure relates to a walk power mower comprising: a grass cutting deck supported upon the ground by a front wheel and a rear wheel, the cutting deck surrounding a grass cutting member, wherein the cutting deck is adapted to traverse the ground in both a forward direction and a reverse direction; at least one transmission adapted to selectively provide driving power to at least one wheel of the front and rear wheels; and a handle comprising first and second laterally spaced-apart and parallel handle members each extending upwardly and rearwardly from the cutting deck. The first and second handle members each comprise: an upper end; and a lower end pivotally attached to the cutting deck such that the handle members pivot about a transverse pivot axis within an operating range of pivotal motion defined by: an upper stop corresponding to the handle being in a first operating orientation; and a lower stop corresponding to the handle being in a second operating orientation, the operating range of pivotal motion being about 5-20 degrees. A control member is carried at or near the upper ends of the first and second handle members, wherein the control member, when moved to a first engaged position, is adapted to place the transmission into operation so that the transmission propels the mower in the forward direction. First and second resilient members are provided and positioned between the deck and the first and second handle members, respectively, the first and second resilient members adapted to bias the first and second handle members to a location at or near the upper stop.

In still another aspect, a walk power mower is provided that includes: a grass cutting deck supported upon the ground by a pair of front wheels and a pair of rear wheels, the cutting deck surrounding at least one grass cutting blade; and a variable speed traction drive system carried on the cutting deck and adapted to selectively provide driving power to at least one wheel of the front and rear pairs of wheels to propel the mower over the ground in both a forward direction and a reverse direction. A handle is also provided and includes first and second laterally spaced-apart and parallel handle members extending upwardly and rearwardly from the cutting deck, wherein the first and second handle members each comprise: an upper end; and a lower end pivotally attached to a rear portion of the cutting deck such that the handle members pivot about a transverse pivot axis within an operating range of pivotal motion defined by an upper stop and a lower stop. The mower also includes a control system carried at or near the upper ends of the first and second handle members, the control system operable to engage the traction drive system to selectively propel the cutting deck in both the forward direction and the reverse direction. First and second resilient members are provided and positioned between the deck and the first and second handle members, respectively. The first and second resilient members are adapted to resiliently deform when the handle members pivot, about the transverse pivot axis, from a position at or near the upper stop toward a position at or near the lower stop.

Yet another aspect of this disclosure relates to a walk power mower which comprises a deck supported by a pair of front wheels and a pair of rear wheels. The deck has at least one grass cutting blade that rotates in a substantially horizontal plane about a substantially vertical axis to cut grass. The deck also has an upwardly and rearwardly extending handle that is gripped by a user who walks on the ground behind the deck to guide and manipulate the deck during motion of the deck over the ground. A prime mover is carried by the deck, the prime mover being operably coupled to the blade for effecting powered rotation of the blade. A variable speed traction drive system is carried on the deck, the prime mover being operably coupled to the traction drive system for effecting powered rotation of the front wheels and the rear wheels. The traction drive system comprises a rear transmission having a rear axle that is operatively connected to the rear wheels for powering the rear wheels to provide self-propelled motion of the deck in a first direction of motion over the ground, a front transmission having a front axle that is operatively connected to the front wheels for powering the front wheels to provide self-propelled motion of the deck in a second direction of motion over the ground that is opposite to the first direction of motion, and a control system carried on the handle that is selectively operable by a user for placing only one transmission at a time into operation so that the rear transmission is active to propel the deck in the first direction while the front transmission is inactive or the front transmission is active to propel the deck in the second direction while the rear transmission is inactive.

Yet another aspect of this disclosure relates to a walk power mower which comprises a traction drive system on a grass cutting deck having a pair of front wheels and a pair of rear wheels. A pair of transmissions power at least one pair of wheels on the deck. A first one of the transmissions provides forward motion of the mower when it is active and a second one of the transmissions provides rearward motion of the mower when it is active. A slidable handle grip is provided on a handle extending upwardly and rearwardly from the cutting deck. The handle grip has a cross bar long enough to be gripped by both hands of the user. The handle grip activates the first one of the transmissions when it is slid downwardly on a handle out of a neutral position thereof as a user walks forwardly holding the cross bar of the handle grip. The handle grip activates the second one of the transmissions when it is slid upwardly on the handle out of the neutral position as a user walks rearwardly holding the cross bar of the handle grip.

BRIEF DESCRIPTION OF THE DRAWINGS

Embodiments of this disclosure will be described more fully in the following Detailed Description, when taken in conjunction with the following drawings, in which like reference numerals refer to like elements throughout.

FIG. 1 is a perspective view of one embodiment of a walk power mower according to this disclosure;

FIG. 2 is an enlarged perspective view of a portion of the handle of the mower of FIG. 1, particularly illustrating the return to neutral system that causes the slidable handle grip of the handle to return to a neutral position in which the traction drive system is disengaged once the user releases the handle grip;

FIG. 3 is a perspective view of the underside of the cutting deck of the mower of FIG. 1, particularly illustrating the dual transmission traction drive system;

FIG. 4 is a perspective view of a portion of a second embodiment of a walk power mower according to this disclosure;

FIG. 5 is an enlarged perspective view of a portion of the handle of the mower of FIG. 4, particularly illustrating a second embodiment of the return to neutral system that causes the slidable handle grip of the handle to return to a neutral position in which the traction drive system is disengaged once the user releases the handle grip;

FIGS. 6A-6B illustrate a mower in accordance with another embodiment of this disclosure, the mower incorporating a biased or “floating” handle, wherein: FIG. 6A is a rear perspective view; and FIG. 6B is a front perspective view;

FIG. 7 is an enlarged view of a portion of the mower of FIGS. 6A-6B;

FIG. 8 is an exploded perspective view of a portion of the mower of FIGS. 6A-6B;

FIG. 9 is a perspective view of a resilient member for use with the mower of FIGS. 6A-6B; and

FIG. 10 is a side elevation view of the mower of FIGS. 6A-6B.

The figures are rendered primarily for clarity and, as a result, are not necessarily drawn to scale. Moreover, various structure/components, including but not limited to fasteners, electrical components (wiring, cables, etc.), and the like, may be shown diagrammatically or removed from some or all of the views to better illustrate aspects of the depicted embodiments, or where inclusion of such structure/components is not necessary to an understanding of the various exemplary embodiments described herein. The lack of illustration/description of such structure/components in a particular figure is, however, not to be interpreted as limiting the scope of the various embodiments in any way. Still further, “Figure x” and “FIG. x” may be used interchangeably herein to refer to the figure numbered “x.”

DETAILED DESCRIPTION

One embodiment of a walk power mower 2 according to this disclosure is illustrated in FIG. 1. Mower 2 comprises a cutting deck 4 that is formed with a generally toroidal cutting chamber 6 that faces downwardly and is open at its bottom. Deck 4 is supported for rolling over the ground by a pair of front wheels 8 and a pair of rear wheels 10. A prime mover 12, such as an internal combustion engine, is carried on top of deck 4. Referring now to FIG. 3, the drive shaft 14 of the prime mover extends vertically downwardly with its lower end extending into cutting chamber 6. A horizontal cutting member or blade 16 is positioned within cutting chamber 6 and is removably secured to the lower end of drive shaft 14 to rotate in a generally horizontal cutting plane to cut grass.

Referring again to FIG. 1, mower 2 is a three-in-one mower having side discharge, rear bagging and mulching modes of operation. In the side discharge mode, a side discharge chute 18 can be mated with a side discharge opening to discharge grass clippings to the side of mower 2 when a side discharge door 20 is opened. In the rear bagging mode, a grass clipping collection bag 22 is mated with a rear discharge opening to collect grass clippings being discharged to the rear of mower 2 when a rear discharge door 24 is opened. While FIG. 1 illustrates deck 4 as being both in the side discharge mode and the rear bagging mode, this is only for the purpose of illustration as these two modes would not be used simultaneously. When side discharge chute 18 is removed and side discharge door 20 is closed and when bag 22 is removed and rear discharge door 24 is closed, mower 2 is placed into its mulching mode in which grass clippings are driven downwardly out of cutting chamber 6 to discharge the clippings beneath mower 2. However, mower 2 need not have multiple modes of operation, but could be built as a single purpose side discharge, rear bagger, or mulching mower.

An upwardly and rearwardly extending handle 26 comprising a pair of laterally spaced handle members or tubes 28 joined by a top cross member 30 may be included as shown. The lower ends of handle tubes 28 are attached to the rear of deck 4. Handle 26 includes a U-shaped handle grip 32 that has a pair of laterally spaced legs 34 connected together by an upper cross bar 36. Legs 34 of handle grip 32 are telescopically received on handle tubes 28 of handle 26 for sliding movement relative thereto. Thus, handle grip 32 is able to slide downwardly on handle tubes 28 as a user walks forwardly while gripping cross bar 36 of handle grip 32 with both of the user's hands.

Handle grip 32 slides downwardly by an amount that depends upon how fast the user walks forwardly. As will be described in more detail hereafter, the extent or amount of downward travel of handle grip 32 controls a traction drive system 38 (see FIG. 3) of mower 2 to vary the forward ground speed of mower 2 to correspond to the user's walking pace. This type of speed controlling, slidable handle grip is used on the Personal Pace® line of walk power mowers manufactured and sold by The Toro Company, the assignee herein. In addition, this type of slidable handle grip is disclosed more fully in U.S. Pat. No. 6,082,083 to Stalpes et al., which patent is hereby incorporated by reference and shall be referred to as “Stalpes” hereafter.

In Stalpes, handle grip 32 is in a neutral, i.e., a drive disengaged position, when handle grip 32 is at the top of handle 26 with handle grip 32 located adjacent to cross member 30 that joins handle tubes 28 together. The only control motion of handle grip 32 in Stalpes is the downward sliding motion that engages the traction drive system of Stalpes in forward and that varies the forward ground speed in concert with the user's forward walking pace. When the user lets go of handle grip 32 in Stalpes, handle grip 32 is spring biased to slide back up handle 26 to return to the top thereof at which point the traction drive system becomes disengaged once again.

In mower 2 of this disclosure, the Stalpes handle grip 32 has been modified so that the neutral position of handle grip 32 is no longer at the top of the range of motion of handle grip 32. Now, the neutral position of handle grip 32 is displaced somewhat downwardly from cross member 30 of handle 26. A return to neutral system 40 maintains handle grip 32 in its now lower neutral position relative to cross member 30 of handle 26.

Handle grip 32 functions as it did in Stalpes when the user grips cross bar 36 of handle grip 32 and walks forwardly, i.e., handle grip 32 slides downwardly in the direction of the arrow A in FIG. 1 to activate traction drive system 38 in forward and to vary the forward ground speed in concert with the user's forward walking pace. Now, however, if the user grips cross bar 36 of handle grip 32 and walks rearwardly, as when pulling mower 2 back, handle grip 32 is now also able to slide upwardly out of neutral rather than being held in neutral as in Stalpes. This upward sliding motion of handle grip 32 is shown by the arrow B in FIG. 1. This activates traction drive system 38 in reverse and varies the reverse ground speed of mower 2 in concert with the user's rearward walking pace. In either forward or reverse powered motion of mower 2, when the user lets go of handle grip 32, return to neutral system 40 causes handle grip 32 to slide back to its centered neutral position between the lower and upper limits of the range of motion of handle grip 32 to disengage traction drive system 38.

Referring now to FIG. 2, return to neutral system 40 comprises a rod 42 having an upper end fixed by a bracket 44 to a laterally extending cross member 46 that is also part of handle grip 32. Rod 42 has spaced upper and lower push nuts 48 _(u) and 48 _(l) fixed thereto to move with rod 42. Push nuts 48 bear respectively against one end of cylindrical, upper and lower, push tubes 50 _(u) and 50 _(l) which are spaced along the length of rod 42 and through which rod 42 slides. Each push tube 50 has an annular thrust surface 52 that is formed as an integral part thereof. Push tubes 50 are assembled in an inverted relationship relative to each other along the length of rod 42 such that thrust surface 52 of upper push tube 50 _(u) is at the lowermost end of upper push tube 50 _(u) while thrust surface 52 of lower push tube 50 _(l) is at the uppermost end of lower push tube 50 _(l).

Return to neutral system 40 further includes a U-shaped clevis 54 fixed to handle 26 with the spaced, parallel side walls 56 of clevis 54 forming an upper wall 56 _(u) and a lower wall 56 _(l). Upper and lower push tubes 50 _(u) and 50 _(l) when assembled on rod 42 are arranged to pass through bores in upper and lower walls 56 _(u) and 56 _(l) of clevis 54 with thrust surfaces 52 on upper and lower push tubes 50 _(u) and 50 _(l) being inside clevis 54 immediately adjacent to upper and lower walls 56 _(u) and 56 _(l) of clevis 54. A compression spring 58 is arranged inside clevis 54 with the ends of spring 58 bearing against thrust surfaces 52 of upper and lower push tubes 50 _(u) and 50 _(l). When return to neutral system 40 is properly adjusted and traction drive system 38 is in neutral, spring 58 will force upper and lower push tubes 50 _(u) and 50 _(l) apart until thrust surfaces 52 thereon abut against the upper and lower walls 56 _(u) and 56 _(l) of clevis 54 and the opposite ends of upper and lower push tubes 50 _(u) and 50 _(l) are immediately adjacent to upper and lower push nuts 48 _(u) and 48 _(l).

When the user pushes down on handle grip 32 to initiate powered forward motion of mower 2, upper push nut 48 _(l) on rod 42 presses down on the upper end of upper push tube 50 _(l) to slide upper push tube 50 _(l) downwardly relative to clevis 54. Note that lower push tube 50 _(l) remains stationary with rod 42 simply sliding through lower push tube 50 _(l) since the lower push nut 48 _(l) moves away from the lowermost end of lower push tube 50 _(l) and lower push tube 50 _(l) remains within clevis 54 since thrust surface 52 on lower push tube 50 _(l) is held in place by its engagement with lower wall 56 _(l) of clevis 54. The downward motion of upper push tube 50 _(l) compresses spring 58 downwardly. Thus, when the user eventually releases handle grip 32, the compressed spring 58 pushes back upwardly on upper push tube 50 _(u) to cause the uppermost end of upper push tube 50 _(u) to push the upper push nut 48 _(u) back upwardly, thereby returning handle grip 32 to its centered neutral position.

Return to neutral system 40 works the same way but in an opposite fashion when handle grip 32 is pulled upwardly in the direction of the arrow B to initiate reverse powered motion of mower 2. This time it is lower push tube 50 _(l) that is pushed upwardly by lower push nut 48 _(l) with upper push tube 50 _(u) remaining stationary. Thus, spring 58 is compressed upwardly. When handle grip 32 is eventually released, the lowermost end of lower push tube 50 _(l) pushes downwardly on lower push nut 48 _(l) as the upward compression of spring 58 is released to slide handle grip 32 back downwardly to return handle grip 32 to its centered neutral position.

Referring now to FIG. 3, traction drive system 38 comprises a first rear transmission 60 _(r) which powers rear wheels 10 of mower 2 and a second front transmission 60 _(f) which powers front wheels 8 of mower 2. Transmissions 60 preferably comprise, but are not limited to, mechanical gear drive transmissions that use various speed reduction stages to reduce the relatively high rotational speed of drive shaft 14 of prime mover 12 to a lower speed suitable for self-propelling mower 2 at ground speeds that match the walking pace of the user. Some of these speed reduction stages are built into the gearing inside the housings of transmissions 60. However, the final speed reduction stage is formed by a small diameter drive gear 62 on each end of an axle 64 of each transmission 60 that drives a larger diameter driven gear 66 fixedly attached to one of wheels 8, 10.

Drive gears 62 on the opposite ends of axle 64 of rear transmission 60 _(r) engage the backsides of driven gears 66 of rear wheels 10. The reverse is true for drive gears 62 for front transmission 60 _(f) which engage the front sides of driven gears 66 of front wheels 8. Thus, when axles 64 of transmissions 60 are rotated in opposite directions by the operation of prime mover 12, front and rear drive wheels 8 and 10 will be rotated in opposite directions relative to each other. For example, if rear drive wheels 10 are rotated in a forward direction to propel mower 2 forwardly, front drive wheels 8 will be rotated in a rearward direction to propel mower 2 in reverse. As a consequence, it should be apparent that only one transmission 60 is active at any given time while the other transmission 60 remains inactive. Either transmission 60 can be selected to be the one that provides forward motion while the remaining transmission 60 will then be the one that provides reverse motion.

Rear transmission 60 preferably has a split axle 64 and provides a differential action to permit rear wheels 10 to be driven at different speeds during a turn, such as when the user swings mower 2 around 180° at the end of a pass when mowing his or her lawn, to avoid tearing or scuffing the grass. Rear wheels 10 may rotate at different speeds during turns using either an unpowered or powered differential. For example, in an unpowered differential which is preferred due to somewhat lower cost, the portion of split axle 64 powering whichever rear wheel 10 is on the outside of the turn simply overruns the rotational speed of the portion of split axle 64 powering the rear wheel 10 on the inside of the turn to create the difference in wheel speed. Since front wheels 8 of mower 2 are typically lifted up off the ground during such a turnaround of mower 2, front transmission 60 preferably has a solid axle and lacks any differential action, thereby reducing overall cost of mower 2.

Each transmission 60 is provided with a one-way clutch that permits the wheels driven by that transmission 60 to free wheel when mower 2 is being propelled in a direction opposite to the direction transmission 60 is designed to operate. In the example where one transmission is active and is driving mower 2 forwardly while the other reverse drive transmission is inactive and is not in operation, the one way clutch in the inactive reverse drive transmission permits the drive wheels coupled to that transmission to rotate freely with respect to the internal gearing of the reverse drive transmission to avoid the drag or resistance such internal gearing would otherwise provide when mower 2 moves forwardly.

Each front and rear transmission 60 _(f) and 60 _(r) is separately driven by its own independent belt drive 68 _(f) and 68 _(r) from drive shaft 14 of prime mover 12. Each transmission 60 is a rocking transmission of the type disclosed in Stalpes. When handle grip 32 is in neutral and both transmissions 60 are inactive, belts 70 in belt drives 68 are sufficiently slack so that the input pulleys on transmissions 60 are stationary even though drive shaft 14 of prime mover 12 is rotating. Effectively, mower 2 is at rest even with the engine running when handle grip 32 is not being pushed or pulled by the user.

However, as the user slides handle grip 32 up or down on handle 26 in either the downward direction A or the upward direction B, this motion rocks one transmission 60 in a direction (rearwardly about its axle 64 for rear transmission 60 _(r) and forwardly about its axle 64 for front transmission 60 _(f)) to tighten drive belt 70 to the rocking transmission while leaving drive belt 70 to other transmission slack. As drive belt 70 to the rocking transmission becomes taut, the transmission becomes active to begin rotating the pair of wheels powered by the rocking transmission. The speed of rotation of axle 64 of the rocking transmission, and thus the ground speed of mower 2, progressively increases as handle grip 32 is moved ever further in the selected direction and the tautness of belt 70 progressively increases. Thus, the ground speed of mower 2 progressively increases from zero to a maximum speed as handle grip 32 travels out of neutral to the end of its range of motion in the selected direction A or B. This enables the ground speed of mower 2 to be matched to the walking pace of the user whether mower 2 is being propelled in forward or reverse.

First and second Bowden cables (not shown) having inner wires carried within outer conduits operably couple handle grip 32 to transmissions 60. The first Bowden cable has a “live cable” setup in which a rear end of the outer conduit is fixed or clamped to handle 26 and the front end of the outer conduit is fixed or clamped to a lower end of one handle tube 28 or to a rear end of deck 4. The rear end of the inner wire of the first Bowden cable is secured to an opening 72 in a pivotal tab 74 (see FIG. 2) that is rotated rearwardly when handle grip 32 is moved downwardly in the direction of arrow A. The front end of the inner wire of the first Bowden cable is then attached to rear transmission 60 _(r) to rock rear transmission 60 _(r) rearwardly during downward motion of handle grip 32 in the direction of arrow A. In this “live cable” setup of the first Bowden cable, the downward motion of handle grip 32 causes the “live” inner wire of the first Bowden cable to slide rearwardly within the outer conduit in order to rock rear transmission 60 _(r) rearwardly while the outer conduit remains fixed in place. The “live cable” setup of the first Bowden cable and its interaction with pivotal tab 74 is shown and described in more detail in the Stalpes patent which has previously been incorporated by reference herein.

The second Bowden cable has a “live conduit” setup in which the front end of the inner wire is fixed or clamped in place to deck 4 and the rear end of the inner wire is fixed or clamped in place to handle grip 32. The rear end of the conduit in the second Bowden cable is fixed or clamped in place to an upper portion of one handle tube 28 adjacent the place where the rear end of the inner wire of the second Bowden cable attaches to handle grip 32. The front end of the conduit in the second Bowden cable is clamped or fixed to front transmission 60 to rock front transmission 60 forwardly during upward motion of handle grip 32 in the direction of arrow B. In this “live conduit” setup, the upward motion of handle grip 32 in the direction of arrow B deforms the shape of the clamped inner wire of the second Bowden cable. This deformation in the shape of the inner wire causes the “live” conduit of the second Bowden cable to slide forwardly over the inner wire to push against front transmission 60 _(f) to rock front transmission 60 _(f) forwardly. Only one Bowden cable applies force to only one transmission at any given time with the other Bowden cable not applying force to the other transmission so that only one transmission at a time is activated.

Mower 2 equipped with traction drive system 38 of this disclosure has powered operation of rear transmission 60 _(r) to propel mower 2 forwardly in a variable speed manner as handle grip 32 is gripped by the user and the user walks forwardly, thereby sliding handle grip 32 downwardly on handle 26 in an amount proportional to the walking pace of the user. However, when trying to pull mower 2 back during a trimming operation or when trying to mow a small patch of grass in reverse, the user no longer has to use manual force to manhandle mower 2 in the reverse direction. Instead, the user merely maintains his or her grip on cross bar 36 of handle grip 32 and walks rearwardly at any desired pace. This will slide handle grip 32 upwardly on handle 26 to initiate powered operation of front transmission 60 to propel mower 2 rearwardly at a variable ground speed commensurate to the walking pace of the user. Thus, the task of operating mower 2 is greatly eased since mower 2 is self-propelled both in forward and reverse while maintaining the functionality of the Personal Pace® control system of The Toro Company that had previously been used only on mowers that were self-propelled in forward only.

The advantages of a mower that is self-propelled in both forward and reverse is achieved in a cost-effective manner by using mechanical, gear drive transmissions that are both durable and inexpensive in comparison to using hydraulic motor/pump combinations or electric motor/drive combinations. Moreover, since transmissions 60 used to drive front and rear wheels 8, 10 are different from one another and are mounted on separate front and rear axles, this allows rear transmission 60 _(r) to have a split axle/differential action configuration while front transmission 60 _(f) has a solid axle/non-differential action configuration. The manner of driving front and rear wheels 8, 10 using the same size drive gears 62 on the ends of the axles of the front and rear transmissions and the same size driven gears 66 on the wheels, but simply reversing which sides of driven gears 66 are engaged by drive gears 62, leads to increased part commonality and thus reduced cost. This allows a powered, reversible mower to be manufactured and sold at a reasonable cost.

Referring now to FIGS. 4 and 5, a second embodiment of a mower according to this disclosure is illustrated generally as 2′. The same reference numerals used in FIGS. 1-3 to refer to components will be used in FIGS. 4 and 5 to refer to the same or corresponding components with a prime designation being used to refer to those components in the second embodiment, e.g. mower 2′ in FIGS. 4 and 5 as opposed to mower 2 in FIGS. 1-3.

Referring now to FIG. 4, in mower 2′ front transmission 60 _(f)′ and its axle 64′ have been relocated from the front to the back of mower 2′ so that only rear wheels 10′ are reversibly driven by the dual transmissions 60 _(f)′ and 60 _(r)′ with such transmissions and their axles being disposed on opposite sides of the axis of rotation of rear wheels 10′. In this embodiment, front wheels 8′ are present but unpowered with only rear wheels 10′ serving to self-propel mower 2′. As in the first embodiment concerning mower 2, only one transmission 60′ (driven by belt 70′ and having a drive gear 62′ engaged with driven gear 66′) is active at any given time while the other transmission 60′ (driven by another belt 70′ and also having a drive gear 62′ engaged with driven gear 66′) remains inactive. Propelling rear wheels 10′ in opposite directions may yield better traction than using front wheels 8′ to drive mower 2′ in the direction that is opposite to the direction that rear wheels 10′ drive mower 2′. This is due to the fact that more of the weight of a mower like mower 2, 2′ is over rear wheels 10′ as compared to front wheels 8′. In addition, the filling of a grass clipping collection bag at the rear of mower 2′ with grass clippings during a mowing operation only accentuates this rearward weight distribution.

In mower 2′ as shown in FIG. 4, whichever transmission 60′ is used to produce forward motion of mower 2′ is preferably one having a split axle/differential feature as described earlier with respect to rear transmission 60 _(r) in mower 2. The other transmission 60′ that is used to produce reverse motion of mower 2′ could also be one having a split axle/differential feature since both transmissions are now being used to power rear wheels 10′. However, since the times at which reverse motion is needed and the distances over which mower 2′ would travel in reverse are much more limited than what is required for forward motion, whichever transmission 60′ propels the mower in reverse could remain a transmission having a solid axle without any differential ability.

In addition to the use of both transmissions 60′ to drive rear wheels 10′, a simplified Bowden cable coupling setup is used in mower 2′ as shown in FIG. 5. In mower 2′, pivotal tab 74′ now has a second opening 76 that is disposed on an opposite side of a horizontal axis of rotation, illustrated as x in FIG. 5, of a pivot rod 78 compared to the location of first opening 72′ in tab 74′. As taught in more detail in Stalpes, tab 74′ is rigidly attached to rod 78 to pivot by virtue of the pivoting motion of rod 78 caused by journaling the ends of rod 78 in the mower handle tubes 28′ while a middle U-shaped portion 79 of rod 78 is captured within a channel 80 in cross member 46′ of slidable handle grip 32′. Again, rod 78 and its interaction with cross member 46′ are detailed more fully in the Stalpes patent which has been incorporated by reference herein.

When the user slides handle grip 32′ downwardly on handle tubes 28′, the portion of tab 74′ having opening 72′ is pivoted rearwardly as described in connection with the operation of mower 2. This pulls rearwardly on the “live cable” setup of the first Bowden cable that is connected to whichever transmission 60′ is arranged to drive mower 2′ forwardly to actuate the forward drive transmission 60′. Whichever transmission 60′ is arranged to drive mower 2′ in reverse is now connected by a “live cable” setup of the second Bowden cable to the newly added second opening 76 in tab 74′. Thus, when the user pulls handle grip 32′ upwardly on handle tubes 28′ as he or she walks in reverse, the portion of tab 74′ having opening 76 is now pivoted rearwardly to actuate the reverse drive transmission 60′. Since both transmissions 60′ are now at the rear of mower 2′, the length of the second Bowden cable run is shortened compared to the length required in mower 2, and a “live cable” rather than a “live conduit” setup of the Bowden cable is used. This simplifies the routing and arrangement of the Bowden cables. However, the operation of mower 2′ is the same as mower 2, namely pushing handle grip 32′ downwardly as the user walks forwardly powers mower 2′ in a forward direction at a speed commensurate to the user's walking pace while pulling handle grip 32′ upwardly as the user walks rearwardly powers mower 2′ in a rearward direction at a speed commensurate to the user's walking pace.

Referring still further to FIG. 5, the use of the double headed tab 74′ as described above to activate both transmission 60 _(f)′ and 60 _(r)′ in mower 2′ permits a simplified return to natural system 40′. All that is required now is the use of one or more torsion springs 82, preferably two such springs 82, surrounding the ends of rod 78 that lie along and define the rotational axis x of rod 78 with such springs being anchored at one end on rod 78 and at the other end on a portion of the adjacent handle tube 28′. When handle grip 32′ is located in its centered, neutral, drive disengaging position, torsion springs 82 are in their unstressed state such that handle grip 32′ is retained in neutral. As rod 78 is rotated about axis x in either one direction or the other due to motion of handle grip 32′ relative to handle tubes 28′, torsion springs 82 get coiled up or twisted in one direction or the other to resist the motion of handle grip 32′ out of neutral. When the user subsequently releases handle grip 32′, the biasing force built up in the coiled torsion springs 82 is now free to act on handle grip 32′ to move it back to neutral.

The return to neutral system 40′ as shown in FIG. 5 is simpler and thus less costly than system 40 shown in FIGS. 1-3 and takes up less space on mower 2′. Thus, the cable coupling setup and return to neutral system 40′ shown in FIG. 5 could be used with mower 2 shown in FIGS. 1-3 if so desired.

FIGS. 6A-10 illustrate a walk power mower 200 in accordance with another embodiment of the present disclosure. With the exceptions noted below, the mower 200 may be mostly identical to the mower 2 (or 2′) already described herein. For example, the mower 200 may include a cutting deck 204 that may be self-propelled, i.e., it may include a variable speed traction drive system having one or more transmission(s) carried by the deck as described herein. The drive system may be capable of selectively providing driving power to one or more of the wheels in both a forward and a reverse direction. Alternatively, the mower 200 may incorporate a conventional transmission (e.g., rear-wheel drive, front-wheel drive, or all-wheel drive) that is capable of selectively providing driving power to one or more of the wheels in only a single (e.g., forward) direction. In yet other embodiments, the mower may lack a transmission (i.e., it may be push-powered only). For brevity, aspects of the mower 200 that are either commonly known in the art, or that are already described herein above, are not further described below.

As shown in FIGS. 6A-6B, the grass cutting deck 204 is supported upon the ground 203 by a pair of ground-engaging front wheels 208 and a pair of ground-engaging rear wheels 210. Again, the traction drive system may drive at least one of the front wheels and/or rear wheels forwardly to propel the mower 200 as it traverses the ground 203 in a forward direction, while the same or different wheel(s) may optionally be driven rearwardly to propel the mower in the reverse direction as already discussed herein. In other embodiments, the wheels of the mower may be undriven, i.e., the mower may move under operator push-power only.

The deck 204 may further support a prime mover 212 such as an electric motor or gasoline-powered engine. The prime mover may power not only the drive wheels of the mower, but also a cutting blade 16 (see FIG. 3) operable to rotate within the deck.

A handle 226 extends upwardly and rearwardly from the deck 204 as shown in FIGS. 6A-6B. As with the handle 26 of the mower 2, the handle 226 may include a pair of laterally spaced-apart and parallel handle members or tubes 228 extending upwardly and rearwardly from the cutting deck. Each handle tube includes an upper end forming a grip area, e.g., cross member 230 and/or handle grip 232. Lower ends of each handle tube 228 may be pivotally attached to the deck 204, e.g., to a rear portion of the deck. While shown as incorporating two parallel handle tubes, mowers with handles formed from a single handle member or tube are also contemplated.

The handle 226 of the exemplary mower 200 may include a U-shaped handle grip 232 having a pair of laterally spaced legs 234 connected by an upper cross bar 236 at or near the upper ends of the handle members. As with the mower 2, legs 234 of the handle grip 232 may be telescopically attached near the upper ends of the handle tubes 228 for sliding movement relative thereto. Thus, handle grip 232, like the grip 32 described above, forms a control system or member slidable downwardly (and optionally upwardly) on the handle tubes 228 as the user walks forwardly (and optionally, rearwardly) while gripping the cross bar 236 with the user's hands. That is to say, the control member of the handle 226 is operable to engage the variable speed traction drive system to selectively propel the cutting deck 204 in one or both of the forward and reverse directions in a manner already described herein with respect to the mowers 2 and 2′.

Of course, in other embodiments, the handle 226 may include an alternative control member for interfacing with the traction drive system to control mower propulsion, or it may completely lack any such control member/traction drive system (i.e., when configured as a push-powered mower).

The lower ends of the handle tubes 228 may pivotally attach to the deck 204 such that the handle 226/handle tubes 228 may pivot about a horizontal transverse pivot axis 250 (e.g., an axis that is transverse to a direction of forward or reverse travel of the deck) as shown in FIG. 7. To accommodate this pivotal connection, the mower 200 may include left and right upright float plates 252 associated with the left and right handle tubes 228, respectively. The plates 252 may each define an aperture operable to receive a fastener (e.g., pin/nut 254) passing through an aligned aperture in its associated handle tube 228. The pins/nuts 254 thus define the pivot axis 250 about which the handle (e.g., handle tubes) may pivot.

Each handle tube 228 may also include a handle latch 256. Each latch may include a lever 258 that is rotatable (e.g., 90 degrees) to allow extension and retraction of a latch pin 260. In the operating position illustrated in FIG. 7, each pin 260 may be engaged with a slot 264 formed in the associated plate 252. The slots constrain the handle 226 (handle members 228) not to a singular position like the notches 262 (described below), but rather allow the handle 226/tubes 228 to pivot, relative to the deck 204, between: an upper stop 266 a (upper end of the slot 264) corresponding to the handle being in a first operating orientation R (see FIG. 10); and a lower stop 266 b (lower end of the slot) corresponding to the handle being in a second operating orientation B (see also FIG. 10). The upper and lower stops 266 a, 266 b thus define an operating range of pivotal motion of the handle (i.e., of the handle tubes). In one embodiment, the operating range of pivotal motion is at least about 5 degrees (i.e., about 5 degrees or more) of rotation about the pivot axis 250. For example, in some embodiments, a range of about 5-20 degrees, or a range of about 8-12 degrees, is contemplated.

By retracting the latch pins 260, the handle 226/handle members 228 may also be moved from the operating orientations to a third or storage orientation S shown in broken lines in FIG. 10. In the storage orientation S, the handle 226/handle tubes 228 is positioned generally vertically to reduce the footprint of the mower during non-use. The handle 226 may be latched in the storage orientation by extending the pins 260 into engagement with associated notches or openings 262 formed on the plates 252 (see FIG. 7). As one can appreciate, the storage orientation S is outside of the operating range of pivotal motion defined by the slots 264 and stops 266 a, 266 b. While shown as placing the handle 226/handle members 228 in a generally vertical storage position, such a configuration is not limiting. For instance, other embodiments may locate the notches 262 (or, alternatively, provide an additional set of notches 262) to allow for handle 226/handle member 228 storage at a different angular orientation. One such orientation may place notches 262 such that the handle 226/handle members 228 extend forwardly and generally parallel to the ground 203 (see FIG. 10) when in a storage orientation S′.

As shown in the exploded view of FIG. 8, each plate 252 may rotatably attached to an upright flange 253 of the mower deck via its associated pin/nut 254 such that it may rotate about the transverse pivot axis 250. To rotationally secure each plate 252 in place relative to its associated flange 253, a fastener 255 and threaded knob 257 may be provided. The fastener 255 may be inserted through an aperture 259 in the flange 253 and into one of two (or more) holes 261 a, 261 b formed in the bracket 252. By pivoting the plate until the appropriate hole 261 a, 261 b aligns with the aperture 259, the mower may provide varying handle operating heights to accommodate a broad range of users. Once the fastener 255 is inserted through the desired hole 261 a or 261 b of each plate 252, the threaded knob 257 may be secured to the fastener 255 to lock the plate 252 in place.

With reference now to FIGS. 7-10, the mower 200 may also include a handle float system adapted to bias the handle (e.g., the handle members) toward the upper stop 266 a. In one embodiment, the float system includes a resilient member, e.g., left and right resilient members 272, operatively positioned between each lower stop 266 b of the cutting deck and its respective handle member 228. For example, in the illustrated embodiment, the left and right resilient members 272 may be positioned such that they abut a lower side of the left and right handle tubes 228, respectively, when the handle is at rest (when the handle is in the operating orientation R (see FIG. 10) and no user loads are applied to the handle). In some embodiments, the resilient members 272 may bias the tubes 228 against their respective upper stops 266 a. However, in other embodiments, the resilient members may be configured to bias the handle members to a location that is at or near (e.g., slightly short of) the upper stops when the handle is at rest.

The term “resilient member,” as used herein, includes most any device that is able to deform, displace (e.g., displace a contained fluid), distort, or contract under load, and then spontaneously return to (or near) its original configuration when the load is removed. Thus, in addition to the neoprene cylinder configuration described below, other resilient members, e.g., a pneumatic spring, a mechanical or fluidic shock absorber, etc., are also contemplated within the scope of this disclosure.

To secure each resilient member 272 in place, the mower deck 204, e.g., the plates 252, may each define a seat 274. In the illustrated embodiment, each seat is formed by a bent tab of its associated plate 252 (see FIG. 8). The seat 274 may define an aperture adapted to receive an integral threaded stud 276 of the member 272 as shown in FIGS. 8 and 9. The stud 276 may pass through the aperture in the seat 274 and be secured relative to the plate 252 with a nut 278.

Each resilient member 272 may be constructed of a resilient elastomeric material. For example, while not wishing to be bound to any specific configuration, each member 272 may be a neoprene disk or cylinder having a durometer of 60 Shore A. In the illustrated embodiment (see, e.g., FIG. 9), the cylinder may have a height of about one inch and a diameter of about 1.25 inches. However, members of other materials, hardness, size, and geometry are certainly contemplated.

During operation of the mower 200 over the ground 203, the handle 226 may be used to control forward propulsion at already described above with reference to the mower 2. For example, as shown in FIG. 10, the user may apply a force 280 that either: displaces the handle grip 232 downwardly along the handle tubes 228 to engage the traction drive system; or, where the mower is push-powered, pushes against the cross member 230 sufficiently to move the mower forwardly. In the case of the former, as the user walks forwardly and applies this input force 280 to the handle grip 232, the handle grip moves from a neutral position (wherein the traction drive system is inactive), to a first engaged position, causing one of the transmissions to engage and propel the mower in the forward direction.

As this user-applied force 280 is offset from the deck 204, it may also produce a pivoting force on the handle 226/handle tubes 228 (about the axis 250 (see also FIG. 7)) in a clockwise direction 282 as shown in FIG. 10. However, the upper stop 266 a of the slot 264 (see also FIG. 7) will effectively limit this pivotal movement of the handle (relative to the deck 204). As stated above, however, some minimal pivotal movement in the direction 282 may be accommodated before contact occurs between the pin 260 and the upper stop 266 a. However, once the hard stop 266 a is contacted, further movement of the handle 226 (relative to the deck) in the direction 282 may be constrained.

When the user instead applies a pulling input force 284 to the mower handle 226 (e.g., directly to the handle grip 232) in a reverse direction, the handle grip 232 may move upwardly along the handle members from the neutral position to a second engaged position. In the second engaged position, the traction drive system may activate for propulsion in the reverse direction. Moreover, as this pulling force occurs, the handle 226/handle members 228 may pivot (about the pivot axis 250) in a counterclockwise direction 286, i.e., toward the lower stop 266 b (see FIG. 7) corresponding to the second operating orientation B of the handle. As this pivotal movement occurs, each handle tube 228 may compress and resiliently deform its associated member 272. As a result, the moment of the handle 226 is reacted, at least initially, by compression of the members 272, allowing substantial downward movement of the handle (e.g., cross member 230/hand grip 232) to occur and be isolated (at least initially) from corresponding upward movement of the mower's front wheels 208. Of course, once the pins 260 bottom out on the hard stop 266 b (see FIG. 7), further movement of the handle 226 in the direction 286 may begin to elevate the mower's front wheels 208.

With a mower 200 like that described herein incorporating two neoprene members 272 as described above, the handle 226 may pivot about its pivot axis 250 (in the direction 286) about 10 degrees from its at rest position R (shown in solid lines in FIG. 10) to a bottom position B before the front wheels 208 would begin to rise. While varying geometries are possible, one embodiment of the mower 200 may use a handle that is roughly 32 inches long (measured from a centerline of the cross member 230 to the pivot axis 250). With this construction, the cross bar 230 may move a linear distance (e.g., along an arc 288) of approximately 5-10 inches, e.g., 6 inches, as the handle tubes move from the upper stop 266 a to the lower stop 266 b (see FIG. 7). Of course, depending on the stiffness/configuration of the members, the weight and weight distribution of the mower, and the magnitude of the force 284, the members may effectively form the lower stops. That is to say, the members 272 may reach a maximum deflection before the pins 260 contact the lower stops 266 b. However, in other embodiments, the members may continue to compress up and until the lower stops 266 b are contacted by their respective pins 260.

Floating handles such as those described herein may thus allow at least some degree of downward movement of the handle to occur without causing associated lifting of the front wheels. As a result, mowers that utilize a sliding control member to initiate rearward propulsion (e.g., like the handle 226 described herein) may permit rearward/downward handle movement without causing front wheel lifting (at least during typical and expected operation). This advantage may be especially useful for mowers that incorporate reverse drive at the front wheel axle. However, even for mowers that provide no powered reverse operation, floating handles in accordance with embodiments of the present disclosure may still assist in keeping the front wheels in contact with the ground during reverse pulling of the mower.

While described herein in the context of a four-wheel mower, such a configuration is exemplary only. For instance, it is contemplated that embodiments of the present disclosure may find application to mowers having tri-wheel configurations (e.g., having only a single front wheel and/or a single rear wheel), as well as to most any other multi-wheel/multi-axle configuration. Yet further, mowers using ground-engaging members other than wheels (e.g., a rear roller) are also possible. Still further, embodiments of the present disclosure may find application to mowers entirely lacking physical ground-engaging members. For example, hover mowers, which float above the ground on a cushion of air generated by the mower, may benefit from the concepts (e.g., the biased handle) described herein. Those of skill in the art will further realize that embodiments of the present disclosure may also find application to walk-behind power equipment other than lawn mowers having a ground-traversing tool housing other than a cutting deck including, for example, aerators, wheeled debris blowers, cultivators, and the like.

Various modifications will be apparent to those skilled in the art. Thus, the scope of this invention is not to be limited to the details of the various embodiments described herein, but shall be limited only by the appended claims, and equivalents thereof. 

1. A walk power mower comprising: a grass cutting deck surrounding a grass cutting member, wherein the cutting deck is adapted to travel over the ground in both a forward direction and a reverse direction; a handle comprising an upwardly and rearwardly extending handle member, wherein the handle member includes: an upper end comprising a grip area; and a lower end pivotally attached to the cutting deck such that the handle member pivots about a transverse pivot axis within an operating range of pivotal motion defined by: an upper stop corresponding to the handle being in a first operating orientation; and a lower stop corresponding to the handle being in a second operating orientation, the operating range of pivotal motion being at least about 5 degrees; and a resilient member operatively positioned between the lower stop and the handle member, wherein the resilient member is adapted to bias the handle member to a location at or near the upper stop.
 2. The mower of claim 1, wherein the resilient member comprises a neoprene cylinder.
 3. The mower of claim 1, wherein the cutting deck comprises a vertical float plate defining the transverse pivot axis.
 4. The mower of claim 3, wherein the float plate is rotatable relative to the cutting deck about the transverse pivot axis.
 5. The mower of claim 3, wherein the resilient member is attached to the float plate.
 6. The mower of claim 3, wherein the float plate defines a slot adapted to receive therein a pin associated with the handle member, wherein ends of the slot define the upper and lower stops.
 7. The mower of claim 6, wherein the pin is adapted to withdraw from the slot such that the handle member can pivot about the transverse pivot axis to a third storage orientation that is outside of the operating range of pivotal motion.
 8. The mower of claim 1, wherein the operating range of pivotal motion is about 8-12 degrees.
 9. The mower of claim 1, wherein the grip area moves a linear distance of about 5-10 inches as the handle member moves between the upper stop and the lower stop.
 10. A walk power mower comprising: a grass cutting deck supported upon the ground by a front wheel and a rear wheel, the cutting deck surrounding a grass cutting member, wherein the cutting deck is adapted to traverse the ground in both a forward direction and a reverse direction; at least one transmission adapted to selectively provide driving power to at least one wheel of the front and rear wheels; a handle comprising first and second laterally spaced-apart and parallel handle members each extending upwardly and rearwardly from the cutting deck, wherein the first and second handle members each comprise: an upper end; and a lower end pivotally attached to the cutting deck such that the handle members pivot about a transverse pivot axis within an operating range of pivotal motion defined by: an upper stop corresponding to the handle being in a first operating orientation; and a lower stop corresponding to the handle being in a second operating orientation, the operating range of pivotal motion being about 5-20 degrees; a control member carried at or near the upper ends of the first and second handle members, wherein the control member, when moved to a first engaged position, is adapted to place the transmission into operation so that the transmission propels the mower in the forward direction; and first and second resilient members positioned between the deck and the first and second handle members, respectively, the first and second resilient members adapted to bias the first and second handle members to a location at or near the upper stop.
 11. The mower of claim 10, wherein the first and second resilient members resiliently deform when the handle is pivoted toward the second operating orientation.
 12. The mower of claim 10, wherein the first and second resilient members isolate downward movement of the handle from upward movement of the front wheel.
 13. The mower of claim 10, further including a second transmission adapted to provide driving power to at least one wheel of the front and rear wheels.
 14. The mower of claim 13, wherein movement of the control member to a second engaged position places the second transmission into operation so that the second transmission propels the mower in the reverse direction.
 15. A walk power mower comprising: a grass cutting deck supported upon the ground by a pair of front wheels and a pair of rear wheels, the cutting deck surrounding at least one grass cutting blade; a variable speed traction drive system carried on the cutting deck and adapted to selectively provide driving power to at least one wheel of the front and rear pairs of wheels to propel the mower over the ground in both a forward direction and a reverse direction; a handle comprising first and second laterally spaced-apart and parallel handle members extending upwardly and rearwardly from the cutting deck, wherein the first and second handle members each comprise: an upper end; and a lower end pivotally attached to a rear portion of the cutting deck such that the handle members pivot about a transverse pivot axis within an operating range of pivotal motion defined by an upper stop and a lower stop; a control system carried at or near the upper ends of the first and second handle members, the control system operable to engage the traction drive system to selectively propel the cutting deck in both the forward direction and the reverse direction; and first and second resilient members positioned between the deck and the first and second handle members, respectively, the first and second resilient members adapted to resiliently deform when the handle members pivot, about the transverse pivot axis, from a position at or near the upper stop toward a position at or near the lower stop.
 16. The mower of claim 15, wherein the variable speed traction drive system comprises a first transmission operable to propel the mower in the forward direction, and a second transmission operable to propel the mower in the reverse direction.
 17. The mower of claim 15, wherein each resilient member is secured relative to the deck such that its associated handle member abuts the resilient member when the handle is at rest.
 18. The mower of claim 15, wherein the operating range of pivotal motion is about 5-20 degrees.
 19. The mower of claim 18, wherein the operating range of pivotal motion is about 8-12 degrees.
 20. A walk power mower comprising: a grass cutting deck supported upon the ground by a pair of front wheels and a pair of rear wheels, the cutting deck surrounding at least one grass cutting blade; a variable speed traction drive system carried on the cutting deck and adapted to selectively provide driving power to one or more wheels of the front and rear pairs of wheels to propel the mower over the ground in both a forward direction and a reverse direction; a handle comprising first and second laterally spaced-apart and parallel handle members extending upwardly and rearwardly from the cutting deck, wherein the first and second handle members each comprise: an upper end; and a lower end pivotally attached to a rear portion of the cutting deck such that the handle members pivot about a transverse pivot axis within an operating range of pivotal motion defined by an upper stop and a lower stop; a slidable handle grip attached to the upper ends of the first and second handle members, the slidable handle grip having a neutral position on the handle corresponding to the traction drive system being inactive, wherein the slidable handle grip is: selectively slidable out of the neutral position and downwardly along the handle members, when a user walks forwardly and pushes against the handle grip, to engage the traction drive system for propulsion of the mower in the forward direction; and selectively slidable out of the neutral position and upwardly along the handle members, when the user walks rearwardly and pulls against the handle grip, to engage the traction drive system for propulsion in the reverse direction; and first and second resilient members positioned between the deck and the first and second handle members, respectively, the first and second resilient members adapted to resiliently compress during downward movement of the handle toward the lower stop, thereby isolating such downward movement of the handle from upward movement of the pair of front wheels. 